US7591203B2 - Control apparatus and control method for vehicle - Google Patents

Control apparatus and control method for vehicle Download PDF

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Publication number
US7591203B2
US7591203B2 US11/657,644 US65764407A US7591203B2 US 7591203 B2 US7591203 B2 US 7591203B2 US 65764407 A US65764407 A US 65764407A US 7591203 B2 US7591203 B2 US 7591203B2
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United States
Prior art keywords
shift
gear
transmission
output shaft
control apparatus
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US11/657,644
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US20070199395A1 (en
Inventor
Tatsuya Ochi
Takashi Okada
Hiroshi Sakamoto
Masato Imai
Tetsuo Matsumura
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Hitachi Ltd
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Hitachi Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0213—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift signals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0213—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift signals
    • F16H2061/0216—Calculation or estimation of post shift values for different gear ratios, e.g. by using engine performance tables
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed- or reversing-gearings for conveying rotary motion
    • F16H59/60—Inputs being a function of ambient conditions
    • F16H59/66—Road conditions, e.g. slope, slippery
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19233—Plurality of counter shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19251—Control mechanism
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19284—Meshing assisters
    • Y10T74/19288—Double clutch and interposed transmission

Definitions

  • the present invention relates to a vehicular control apparatus and a vehicular control method, particularly to a control for an automatic transmission.
  • twin clutch type automatic transmission has two clutches and multiple gear trains. Any one of the two clutches are selectively connected to an engine, and any one of the multiple gear trains are selected by a gear selection apparatus, so that the selected gear train connects between an output shaft of the selected clutch and an output shaft of the transmission. Then, one of the clutches is engaged, and another is disengaged to form a desired gear position (for example, see Japanese Patent Laid-Open No. 1994-221347).
  • the so-called pre-shift is executed as follows to shorten a time required for shifting, and to mechanically protect a rotation synchronization mechanism.
  • a predetermined gear selection apparatus Prior to determination and execution of the next shifting, a predetermined gear selection apparatus executes the pre-shift operation that connects between the output shaft of a currently disengaged clutch (which is not driven) and the output shaft of a transmission via a predetermined gear train in order to make the next shifting (gear position) stand by while keeping a currently executed shifting.
  • a data table having the same structure as the so-called shift line for a throttle opening and a vehicle speed is set in advance. Then, in accordance with an amount of operation of an accelerator by a driver, an up shift prediction area or a down shift prediction area is determined to select a pre-shift gear (for example, see Japanese Patent Laid-Open No. 1998-318361).
  • the present invention is to keep down a delay of a shifting response due to failure in a pre-shift gear selection, by improving an accuracy of prediction about the next shifting to be pre-shift.
  • An automatic transmission control of the present invention is characterized in by: acquiring external information required for vehicular transmission control; and selecting a predetermined gear train among plural gear trains of the transmission for executing a pre-shift in accordance with the external information.
  • an accuracy of prediction about shifting is improved. Thereby, a delay of a shifting response due to failure in a pre-shift gear selection can be kept down.
  • FIG. 1 is a system structure diagram showing a main portion of a vehicular control apparatus for a vehicle having a twin clutch type transmission of a first embodiment of the present invention
  • FIG. 2 is a skeleton diagram showing the twin clutch type transmission of the first embodiment of the present invention
  • FIG. 3 is a control block diagram showing a transmission control apparatus 100 of the first embodiment of the present invention.
  • FIG. 4 is a schematic diagram of a data map for a pre-shift gear selection for an automatic shifting mode
  • FIG. 5 is a schematic diagram of a data map for a pre-shift gear selection for a manual shifting mode
  • FIG. 6 is an external view of shifting mode switch means 105 of the first embodiment of the present invention.
  • FIG. 7 is a flowchart showing main processes of the transmission control apparatus 100 of the first embodiment of the present invention.
  • FIG. 8 is a flowchart explaining a pre-shift gear selection section in the automatic shifting mode
  • FIG. 9 is a flowchart explaining a pre-shift gear selection section in the manual shifting mode
  • FIG. 10 is a time chart explaining a main portion of a control of the transmission control apparatus 100 ;
  • FIG. 11 is a time chart explaining a main portion of a control of the transmission control apparatus 100 ;
  • FIG. 12 is a time chart explaining a main portion of a control of the transmission control apparatus 100 ;
  • FIG. 13 is a system structure diagram showing a main portion of a vehicular transmission control apparatus for a vehicle having a twin clutch type transmission of a second embodiment of the present invention.
  • FIG. 14 is a flowchart showing main processes of the transmission control apparatus 100 of the second embodiment of the present invention.
  • This embodiment relates to a vehicular control apparatus in which a twin clutch type transmission having a function for switching between an automatic shifting mode and a manual shifting mode is mounted. Particularly, this embodiment relates to a control for the aforementioned so-called pre-shift.
  • a control apparatus and a control method for a vehicle having a twin clutch type transmission of a first embodiment of the present invention is explained below.
  • the control method can be switched with a shifting mode switch provided to a driver's seat.
  • a shifting instruction concerning up shift/down shift is automatically produced by a program stored in a microcomputer in the automatic shifting mode. Therefore, in a case of the automatic shifting mode, a driver may not feel a pre-shift executed prior to shifting. Accordingly, even when a failure of the pre-shift occurs, for example, a down shift instruction is actually produced in spite of the fact that the pre-shift is executed as an up shift standby, the driver may not feel the fact of the delay in the shifting response due to time loss for re-engagement of the gear to be executed the shifting.
  • FIG. 1 is a system structure view of a main portion of the control apparatus for the vehicle having the twin clutch type transmission applied in the first embodiment of the present invention.
  • an engine 1 as a driving power source, a gear type transmission 2 , a first clutch 3 a , a second clutch 3 b , a final gear 7 , a differential gear 8 , and a driving wheel 9 is shown.
  • the first clutch 3 a is used for gear trains of even gear trains (2nd gear position, 4th gear position, and 6th gear position) and a reverse gear position, in the gear type transmission 2 comprising forward six gear positions and one reverse gear position.
  • the second clutch 3 b is connected to odd gear trains (1st gear position, 3rd gear position, and 5th gear position).
  • Driving torque from the engine 1 is given to the gear type transmission 2 via the first clutch 3 a or second clutch 3 b .
  • the torque is transferred from the final gear 7 and differential gear 8 to the driving wheel 9 via a predetermined gear train and a shaft corresponding to a selected gear position.
  • the gear type transmission is explained later in detail.
  • a structure of the electronic system includes a transmission control apparatus 100 , an engine control apparatus 200 , and a navigation control apparatus 300 .
  • the three control apparatuses execute various information exchange through two-way data communications.
  • the transmission control apparatus 100 is equipped with an accelerator position sensor 101 , a speed sensor 102 for clutch-output shaft, a speed sensor for a transmission output (vehicle speed sensor) 103 , a shift position sensor (gear position sensing means) 104 , a brake switch 105 , a shift lever switch 106 , a mode switch 107 , a clutch actuator 4 , and a shift actuator 5 .
  • the accelerator position sensor 101 senses an amount of an operation of an accelerator by a driver, and outputs the sensed signal to the transmission control apparatus 100 .
  • the clutch output shaft-speed sensor 102 senses an output shaft speed of the first clutch 3 a and an output shaft speed of the second clutch 3 b , and outputs the sensed signals to the transmission control apparatus 100 .
  • the transmission output shaft-speed sensor 103 senses a speed of the output shaft of the gear type transmission 2 , and outputs the sensed signal to the transmission control apparatus 100 .
  • the shift sensor 104 senses a shift position for forming a predetermined gear position by use of the shift actuator 5 , and outputs the sensed signal to the transmission control apparatus 100 .
  • the brake switch 105 senses whether a driver operates a brake, and outputs the sensed signal to the transmission control apparatus 100 .
  • the shift lever switch 106 senses a position of a shift lever operated by the driver, e.g., in a case of switching between forward and reverse, and outputs the sensed signal to the transmission control apparatus 100 .
  • the shifting mode switch 107 senses an automatic shifting mode or a manual shifting mode selected by the driver, and outputs the sensed signal to the transmission control apparatus 100 .
  • the clutch actuator 4 performs engagement and disengagement of the first clutch 3 a and the second clutch 3 b respectively in accordance with a control instruction from the transmission control apparatus 100 , so that power from the engine 1 is transferred and interrupted to the output shaft of the transmission. Further, the clutch actuator 4 switches torque between both clutches to achieve shifting while the vehicle is traveling.
  • the shift actuator 5 is the above-described gear selection apparatus.
  • the shift actuator 5 selectively operates a 1st-3rd shift fork (not shown), a 5th shift fork (not shown), a 2nd-4th shift fork (not shown), and a 6th-reverse shift fork (not shown).
  • the clutch-output shaft and the transmission-output shaft are connected to each other to form a predetermined gear position.
  • a predetermined gear train connected to a non-driven side is operated prior to an execution of the next shifting to achieve the pre-shift.
  • the engine control apparatus 200 is equipped with an accelerator position sensor 201 , a throttle opening sensor 202 , and an electronic throttle device 6 .
  • the accelerator position sensor 201 senses an amount of an operation of an accelerator by the driver, and outputs the sensed signal to the engine control apparatus 200 .
  • the throttle opening sensor 202 senses an opening of a throttle valve of the electronic throttle device 6 , and outputs the sensed signal to the engine control apparatus 200 .
  • the electronic throttle 6 controls the opening of the throttle valve provided to an engine intake system in accordance with a control instruction from the engine control apparatus 200 .
  • the transmission control apparatus 100 sends a required-torque instruction to the engine control apparatus 200 .
  • the engine control apparatus 200 operates the electronic throttle device 6 or changes an ignition timing in accordance with the received required-torque instruction. Accordingly, driving torque generated by the engine 1 can be controlled.
  • the navigation control apparatus 300 is equipped with a direction sensor 301 , a GPS sensor 302 , and a vehicle speed sensor 303 .
  • the direction sensor 301 senses a direction of a vehicle, and outputs the sensed signal to a navigation control apparatus 300 .
  • the GPS sensor 302 senses a GPS signal from a GPS satellite (not shown), and outputs the sensed signal to the navigation control apparatus 300 .
  • the vehicle speed sensor 303 senses a rotation speed of a wheel, and outputs the sensed signal to the navigation control apparatus 300 .
  • the navigation control apparatus 300 calculates a current position where a vehicle is traveling, through a known method by use of the signals of the above sensors.
  • Various map information stored in a storage section built in the navigation control apparatus 300 such as a radius of curvature and road gradient at the current position on a vehicle path, is read, and sent to the transmission control unit 100 by use of the two-way data communications.
  • the transmission control unit 100 controls the shift actuator 5 prior to the next shifting, by use of the map information corresponding to a current position calculated in the navigation control apparatus 300 , to execute the pre-shift.
  • the main portion of the control apparatus for the vehicle including the twin clutch type transmission is structured as described above, so that an accuracy of prediction about shifting in the manual shifting mode can be improved, and a delay of shifting due to failure in the pre-shift gear selection can be kept down.
  • FIG. 2 is a skeleton diagram showing the twin clutch type transmission of the first embodiment of the present invention.
  • the engine 1 is directly connected to the clutches 3 with a twin clutch 3 a , 3 b .
  • the first clutch 3 a is connected to its output shaft 41 a directly.
  • the second clutch 3 b is connected to its output shaft 41 b directly.
  • the second clutch-output shaft 41 b is made of a hollow shaft.
  • the first clutch-output shaft 41 a is put through the hollow portion of the second clutch output shaft 41 b , and can rotate without relation of the second clutch output shaft 41 b .
  • a 2nd drive gear 52 , a 4th drive gear 54 , and a 6th drive gear 56 are fixed on the first clutch-output shaft 41 a to be an input shaft of the transmission, and these gears are capable of rotating together with the first clutch-output shaft 41 a without relation of the second clutch-output shaft 41 b .
  • a 1st drive gear 51 , a 3rd drive gear 53 , a 5th drive gear 55 , and a reverse drive gear (not shown) are fixed to the second clutch output shaft 41 b , and these clutches are capable of rotating without relation of the first output shaft 41 a .
  • a first clutch-speed sensor 102 a is attached to the 2nd drive gear 52 to sense a speed of its output shaft.
  • a second clutch speed sensor 102 b is attached to the 1st drive gear 51 to sense a speed of its output shaft.
  • a 1st driven gear 61 , a 2nd driven gear 62 , a 3rd driven gear 63 , a 4th driven gear 64 , a 5th driven gear 65 , a 6th driven gear 66 , and a reverse driven gear (not shown) are mounted freely on the transmission-output shaft 42 .
  • a first mesh clutch 70 a having a rotation synchronization mechanism is provided between the 1st driven gear 61 and the 3rd driven gear 63 .
  • the shift actuator 5 (not shown) is controlled to operate the 1st-3rd shift fork for moving the first mesh clutch 70 a in the left and right directions. Accordingly, the 1st driven gear 61 or 3rd driven gear 63 can be connected to the transmission-output shaft 42 . Rotation torque transferred from the 1st drive gear 51 or 3rd drive gear 53 to the 1st driven gear 61 or 3rd driven gear 63 is transferred to the transmission-output shaft 42 via a first mesh clutch 70 a.
  • a second mesh clutch 70 b for the 5th driven gear 65 is provided on the output shaft 42 .
  • the shift actuator 5 (not shown) is controlled to operate the 5th shift fork for moving the second mesh clutch 70 b in the right direction. Accordingly, the 5th driven gear 65 can be connected to the output shaft 42 .
  • a third mesh clutch 70 c is provided between the 2nd driven gear 62 and 4th driven gear 64 .
  • the shift actuator 5 (not shown) is controlled to operate the 2nd-4th shift fork for moving the third mesh clutch 70 c in the left and right directions. Accordingly, the 2nd driven gear 62 or 4th driven gear 64 can be connected to the output shaft 42 .
  • a forth mesh clutch 70 d is provided between the 6th driven gear 66 and reverse driven gear (not shown).
  • the shift actuator 5 (not shown) is controlled to operate the 6th-reverse shift fork for moving the forth mesh clutch 70 d in the left and right directions. Accordingly, the 6th driven gear 66 or reverse driven gear can be connected to the output
  • the output shaft speed sensor 103 is provided to the 1st driven gear 61 , and senses a speed of the transmission-output shaft 42 .
  • the shift actuator 5 selects the corresponding shift fork to operate one of the above mesh clutches. Thereby, the pre-shift is achieved.
  • a shifting instruction is produced in the transmission control apparatus 100 , it is determined whether the operation of the corresponding mesh clutch is complete. When the operation is complete, the clutch actuator 4 is operated to the engagement and disengagement for the first clutch 3 a and second clutch 3 b . Then, actual shifting is executed.
  • FIG. 3 is a control block diagram showing a main portion of the transmission control apparatus 100 of the first embodiment of the present invention.
  • the transmission control apparatus 100 comprises a pre-shift gear selection section 110 for an automatic shifting mode, a pre-shift gear selection section 120 for a manual shifting mode, and a selection switch section 130 .
  • the automatic shifting mode pre-shift gear selection section 110 selects a pre-shift gear position for the automatic shifting mode in accordance with an accelerator position APS sensed by the accelerator position sensor 101 and a vehicle speed VSP calculated from a signal sensed by the transmission output shaft speed sensor 103 . Concretely, as shown in FIG. 4 , by use of a data map having a horizontal axis for the vehicle speed VSP and a vertical axis for the accelerator position APS, it is determined whether a driving area is one where an up shift standby or a down shift standby is to be executed.
  • the above data map can be set for each current gear position of the driving shaft separately.
  • the above current gear position is determined in the transmission control apparatus 100 by use of a signal of the shift position sensor 104 .
  • the manual shifting mode pre-shift gear selection section 120 shown in FIG. 3 selects a pre-shift gear position in accordance with external information acquired in an external information acquisition section 400 .
  • the external information acquisition section 400 comprises the navigation control apparatus 300 , but it is not limited to the navigation control apparatus 300 .
  • the external information acquisition section 400 may comprise, e.g., a radar apparatus for measuring a distance between one's own vehicle and the one ahead, and a camera apparatus for taking in an image of a surrounding of a vehicle, or a communications section for communicating with an external of the vehicle.
  • the above external information may comprise a radius of curvature, a load gradient, a distance between one's own vehicle and the one ahead, or information about a freezing road.
  • a driving area is in the up shift standby area or down shift standby area. Namely, regardless of an accelerator operation by a driver, when a radius of curvature is small, it is determined that the driving area is in the up shift standby area, and when a radius of curvature is large, it is determined that a driving area is in the down shift standby area.
  • the above data map can be set for each current gear position of the driving shaft separately.
  • the selection switch section 130 shown in FIG. 3 decides whether to adopt either computation method by the automatic transmission mode pre-shift gear selection section 110 or the manual transmission mode pre-shift gear selection section 120 .
  • the computation method of the pre-shift gear selection means is switched.
  • the shift lever comprises a P range for parking a vehicle, an R range for reversing the vehicle, an N range in which the vehicle is not driven, and a D range for forwarding the vehicle.
  • an M range can be selected.
  • the shift lever is operated as described above to input a signal of the mode switch 106 (not shown) contained in the shift lever to the transmission control apparatus 100 , so that the shifting mode is switched between the automatic shifting mode and manual shifting mode.
  • the main portion of the transmission control apparatus 100 is structured as described above, so that an accuracy of prediction about shifting can be improved, and a delay of shifting due to failure of the pre-shift selection can be kept down.
  • the radius of curvature Rc received from the navigation control apparatus 300 although is used as a condition for selecting gear to be used for the pre-shift in the above manual shifting mode, such information used for the pre-shift gear selection is not limited to it.
  • the navigation control apparatus 300 calculates a distance from a present location to an approaching road curve, which has a radius of curvature equal to or under a predetermined value, and the distance may be used as the condition for selecting gear to be used for the pre-shift.
  • a radius of curvature in a road under vehicle traveling may be obtained by a camera apparatus, and a value of the radius of curvature may be used for selecting gear to be used for the pre-shift.
  • a camera apparatus a vehicle mounted camera for originally taking in an image concerning a scene ahead of the vehicle may be adopted.
  • information from a vehicle mounted radar apparatus which originally is used for measuring a distance between one's own vehicle and the one ahead vehicle, may be adopt for the pre-shift.
  • FIG. 7 is a flowchart showing main processes of the transmission control apparatus 100 of the first embodiment of the present invention.
  • Step S 71 a signal of the mode switch 106 is took in to determine whether the shifting mode selects the automatic shifting mode. When the determination is YES, the flow goes to Step S 72 . Then, a process in Step 72 is executed. When the determination is NO, the flow goes to Step S 73 . Then, a process in Step 73 is executed.
  • Step S 72 a pre-shift gear is selected for the automatic shifting mode as shown in FIG. 4 . A pre-shift gear position is selected in accordance with an accelerator operation by a driver. Concrete processes of the automatic shifting mode pre-shift gear selection executed in Step S 72 are explained in reference to FIG. 8 .
  • FIG. 8 is a flowchart for the automatic shifting mode pre-shift gear selection.
  • Step S 81 it is determined whether a current gear position of a currently traveling vehicle is in the 1st gear position.
  • the current gear position is determined by use of a signal sensed in the shift position sensor 104 .
  • Step S 82 the flow goes to Step S 82 .
  • Step S 83 the flow goes to Step S 83 .
  • Step S 82 in accordance with a data map for the 1st gear, it is determined whether a driving area is in the up shift area or down shift area.
  • Step 83 it is determined whether the current gear position is in the 2nd gear position.
  • Step S 84 determines when the driving area is in the up shift area or down shift area in accordance with a data map for the 2nd gear position. The same processes as above are executed for 3rd to 6th gear positions.
  • Step S 87 it is determined whether to execute the up shift standby.
  • Step S 88 the flow goes to Step S 89 .
  • Step S 88 the pre-shift gear position is calculated by incrementing the current gear position.
  • Step S 89 it is determined whether to execute the down shift standby.
  • Step S 90 calculate the pre-shift gear position calculated by decrementing the current gear position. Then, the processes of the automatic shifting mode pre-shift gear selection are complete.
  • FIG. 9 is a flowchart of the manual shifting mode pre-shift gear selection means. This process flow uses the same process form as the automatic shifting mode. In this process flow, a current gear position is determined, and it is determined whether the pre-shift gear position in the manual shifting is in a position for the up shift standby or down shift standby by use of a data map for each gear position.
  • the concrete data maps in the manual shifting mode are structured as shown in FIG. 5 . For example, it is determined whether a driving area is in the up shift standby area or down shift standby area in accordance with a radius of curvature of a traveling rode.
  • Steps S 97 to S 100 the current gear position is incremented in the case of the up shift standby, and the current gear position is decremented in the case of the down shift standby.
  • the pre-shift gear position is calculated as described above, and the process flow for the manual shifting mode pre-shift gear selection ends.
  • the main process of the transmission control apparatus 100 is structured as shown in FIGS. 7 to 9 , so that the an accuracy of prediction of shifting in the manual shifting mode can be improved, and a delay of the shifting due to failure of the pre-shift gear selection can be kept down.
  • FIG. 10 is a time chart explaining a main portion of a control of the transmission control apparatus 100 when a pre-shift gear is selected properly.
  • FIG. 10 shows a current gear position and a pre-shift gear position;
  • (B) shows a shift position sensed by the shift position sensor 104 attached to the above-described each shift fork;
  • (C) shows a target torque instruction of the first clutch 3 a and the second clutch 3 b ; and
  • (D) shows an engine speed and the two clutch output shaft speeds.
  • FIG. 10 shows that a 3rd-to-4th up-shift instruction is issued at a time t 0 when a current gear position is in the 3rd gear position, and a pre-shift gear position is in the 4th gear position because of the determination of executing the up shift.
  • so-cold clutch to clutch is executed, namely the clutches are switched at the same time as the issue of the shifting instruction, and the shifting is done promptly, because the pre-shift gear is selected properly.
  • the target torque of the second clutch 3 b having been used for the driving shaft until now is decreased, and the target torque of the first clutch 3 a for having been used for the non-driving shaft until now is increased.
  • the clutch to clutch operation is completed.
  • the switch of the clutches is completed at a time t 1
  • the engine speed changes toward a speed of the first clutch output shaft because the engine speed is restrained by a speed of the first clutch 3 a .
  • the shifting operations are completed.
  • an update of the pre-shift gear position is prohibited.
  • the pre-shift gear position is updated from the 4th gear position to 5th gear position.
  • the 5th shift position is rendered from a neutral position (SF_N) to a 5th engagement position (SF_H).
  • SF_N neutral position
  • SF_H 5th engagement position
  • FIG. 11 is a time chart explaining the main portion of a control of the transmission control apparatus 100 when the pre-shift gear is incorrectly selected.
  • the content of (A) to (D) in FIG. 11 is the same as that in FIG. 10 .
  • FIG. 11 shows a case where a down shift instruction from the 3rd gear position to 2nd gear position is issued at the time t 0 in spite of the fact that the pre-shift gear position is in the 4th gear position because of the determination of up shift.
  • the 2nd-4th shift position is switched from a 4th engagement position (SF_L) to a 2nd engagement position (SF_H) because the pre-shift gear has been incorrectly selected.
  • the clutches are operated to start actual shifting. First, target torque of the second clutch 3 b having been used for the driving shaft until now is decreased, and the engine speed is increased. When it is determined that the engine speed has increased to a speed corresponding to the 2nd gear at the time T 2 , target torque of the second clutch 3 b is decreased, and target torque of the first clutch 3 a having been used for the non-driving shaft until now is increased. Then, the clutches are switched, so called clutch to clutch is executed. When it is determined that operation of clutch to clutch is completed at the time t 3 , the pre-shift gear position is updated from the 4th gear position to 3rd gear position.
  • the 1st-3rd shift position has been already in the 3rd gear engagement position (SF_L), the 1st-3rd shift position does not change.
  • the pre-shift gear is incorrectly selected, the actual shifting can not start during from the time t 0 to t 1 . Therefore, the shifting response is delayed to make a driver feel uncomfortable.
  • FIG. 12 is a time chart explaining the main portion of a control of the transmission control apparatus 100 when a pre-shift gear is selected in the manual shifting mode.
  • (A) shows a current gear position and a pre-shift gear position
  • (B) shows a shift position sensed by the shift sensor 104 attached to each of the above shift forks
  • (C) shows a radius of curvature of a traveling road (the radius of curvature is calculated in the navigation control apparatus 300 )
  • (D) shows an accelerator position, which is an amount of an operation of accelerator by a driver, the amount being sensed in the accelerator position sensor 101 .
  • FIG. 12 shows a current gear position and a pre-shift gear position
  • (B) shows a shift position sensed by the shift sensor 104 attached to each of the above shift forks
  • (C) shows a radius of curvature of a traveling road (the radius of curvature is calculated in the navigation control apparatus 300 )
  • (D) shows an accelerator position, which is an amount of an
  • FIG. 12 is a time chart indicating that a vehicle enters and passes a curved section of a road when a current position is in the 3rd gear position, and a pre-shift gear position is in the 4th gear position because of the determination of executing the up shift.
  • a radius of curvature is decreased, and the vehicle is approaching the curved section ahead. It is determined that the radius of curvature is under Rc_CHG, which is a border between the up shift standby area and the down shift standby area shown in FIG. 5 , at the time t 1 .
  • the pre-shift gear position is updated from the 4th gear position to 2nd gear position.
  • the 2nd-4th gear shift position is rendered from a 4th engagement position (SF_L) to 2nd engagement position (SF_H) to execute the down shift standby.
  • the down shift standby is executed before the driver determines to enter the curved section and operates the accelerator to decelerate the vehicle.
  • the pre-shift gear is updated from the 2nd gear position to 4th gear position.
  • the 2nd-4th shift position is rendered from the 2nd engagement position (SF_H) to 4th engagement position (SF_L) to execute the up shift standby.
  • the up shift standby is executed before the driver determines to pass the curved section and operates the accelerator to accelerate the vehicle again.
  • the transmission control apparatus 100 is controlled as described above, so that an accuracy of prediction about the shifting in the manual shifting mode can be improved, and a delay of the shifting due to failure of the pre-shift selection can be kept down.
  • FIG. 13 is a system structure diagram showing a main portion of the vehicular control apparatus for the vehicle having the twin clutch type transmission of the second embodiment of the present invention.
  • the system structure diagram of FIG. 13 has the same main structure as the first embodiment shown in FIG. 1 .
  • FIG. 13 shows an engine 1 , which is a driving source of a vehicle, a gear type transmission 2 , a first clutch 3 a , a second clutch 3 b , a final gear 7 , a differential 8 , a driving wheel 9 , and a brake actuator 10 .
  • the first clutch 3 a is used for gear trains of even gears (2nd gear, 4th gear, and 6th gear) and a reverse gear position.
  • total gear trains of the gear type transmission 2 is comprised of six forward gear positions and one reverse gear position.
  • the second clutch 3 b is used for odd gears (1st gear, 3rd gear, and 5th gear).
  • Driving torque produced in the engine 1 is inputted to the gear type transmission 2 via the first clutch 3 a or second clutch 3 b , and transferred via a predetermined gear train, a shaft corresponding to each gear position, the final gear 7 and differential 8 to the driving wheel 9 .
  • the brake actuator 10 is controlled, so that a braking force of the vehicle can be changed without an operation of a brake by a driver.
  • the electronic control system includes a transmission 100 , an engine control apparatus 200 , and a distance between vehicles-control apparatus 500 .
  • various data can be communicated to each other by use of two-way data communications.
  • the distance between vehicles-control system includes a radar apparatus 501 , a speed sensor 502 , and a switch 503 for distance between vehicles control.
  • the radar apparatus 501 senses the distance between one's vehicle and the one ahead, and outputs the sensed signal to the control apparatus 500 .
  • the speed sensor senses a speed of the wheel, and outputs the sensed signal to the control apparatus 500 .
  • the switch 503 senses a driver's intention of executing a control for the distance between vehicles, and outputs the detected signal to the control apparatus 500 .
  • the control apparatus 500 controls the vehicle so that the distance between vehicles sensed in the radar apparatus 501 follows a previously set distance.
  • the engine control apparatus 200 operates the electronic throttle apparatus 6 or changes an ignition time in accordance with the received required torque instruction. Then, driving torque produces by the engine 1 is increased or decreased.
  • the engine control apparatus 200 receives a shifting instruction, the engine control apparatus 200 operates the clutch actuator 4 and the shift actuator 5 in accordance with the received shifting instruction to achieve the shifting.
  • the control apparatus 500 for the distance between vehicles automatically controls a driving force and a braking force of the vehicle.
  • a control response to the deceleration is more important. Therefore, in the transmission control apparatus 100 , when being determined that the control for the distance between vehicles is being executed, the pre-shift gear position is in a position for the down shift standby.
  • the transmission control apparatus 100 is controlled as described above, so that the control response to the deceleration during the distance between vehicles can be improved, and the vehicle can be controlled to be more safe.
  • FIG. 14 is a flow chart showing main processes of the transmission control apparatus 100 of the second embodiment of the present invention.
  • Step S 41 a signal of the switch 503 for the distance between vehicles is received from the control apparatus 500 by use of the two-way communications to determine whether the control for the distance between vehicles is being controlled.
  • Step S 42 the flow goes to Step S 42 , and the normal pre-shift gear selection control shown in FIG. 7 is done.
  • the flow goes to Step S 43 , and the down shift standby is always executed regardless of a driving condition of the vehicle, such as an amount of an operation by a driver and a vehicle speed.
  • Step S 45 it is determined whether to execute the up shift standby.
  • Step S 46 the flow goes to Step S 47 .
  • Step S 47 the pre-shift gear position is calculated by incrementing the current gear position.
  • Step s 47 it is determined whether to execute the down shift standby.
  • the flow goes to Step S 48 , and the pre-shift gear position is calculated by decrementing the current gear position. Then, the process flow for the pre-shift gear selection is complete.
  • the main processes of the transmission control apparatus 100 is structured as described above, so that the control response to the deceleration during control of the distance between vehicles can be improved, and the vehicle can be controlled to be more safe.
  • the structure of the vehicular control apparatus for the vehicle having the twin clutch type transmission is as follows.
  • the twin clutch type transmission has the switch function for switching between the automatic shifting mode and manual shifting mode.
  • the twin clutch type transmission operates the multiple gear trains selected by the gear selection apparatus to connect between the output shaft of the selected clutch (which is connected to the output shaft of the engine) and the output shaft of the transmission.
  • one of the clutches is engaged, and another is disengaged to form a desired gear position.
  • the vehicular control apparatus has the pre-shift gear selection section and the external information acquisition section.
  • the pre-shift gear selection section connects an output shaft of the currently non-used clutch (disengaged clutch) and the output shaft of the transmission to each other via a predetermined gear train to be predicted as the next gear position, and makes the next gear shifting standby.
  • the external information acquisition section acquires external information required for vehicle traveling.
  • the pre-shift gear selection section selects a predetermined gear train for the pre-shift in accordance with the acquired external information. In this structure, an accuracy of prediction about the shifting in the manual shifting mode can be improved, and a delay of the shifting due to failure of the pre-shift gear selection can be kept down.
  • the external information acquisition section preferably comprises at least one of the navigation apparatus, a radar apparatus, a camera apparatus, and a communication device for communicating with the external system outside the vehicle.
  • the navigation apparatus preferably comprises at least one of the navigation apparatus, a radar apparatus, a camera apparatus, and a communication device for communicating with the external system outside the vehicle.
  • the pre-shift gear selection section has the first pre-shift gear selection section executed in the automatic shifting mode and the second pre-shift gear selection section executed in the manual shifting mode.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
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US8225687B2 (en) 2009-09-09 2012-07-24 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8429994B2 (en) 2009-09-09 2013-04-30 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
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US8443687B2 (en) 2009-12-14 2013-05-21 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
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US20110168510A1 (en) * 2010-01-11 2011-07-14 Gm Global Technology Operations, Inc. Hydraulic control systems for dual clutch transmissions
US8402855B2 (en) 2010-01-11 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8567580B2 (en) 2010-01-22 2013-10-29 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US20110180364A1 (en) * 2010-01-22 2011-07-28 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
DE102011010890B4 (de) * 2010-02-17 2014-07-24 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Hydraulisches Steuersystem für ein Doppelkupplungsgetriebe
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US8413777B2 (en) 2010-02-17 2013-04-09 GM Global Technology Operations LLC High efficiency hydraulic transmission control system
US20110198180A1 (en) * 2010-02-17 2011-08-18 Gm Global Technology Operations, Inc. Hydraulic control system for a dual clutch transmission
US20130312556A1 (en) * 2010-08-12 2013-11-28 Schaeffler Technologies AG & Co. KG Method for operating an automated dual-clutch transmission
US9243688B2 (en) * 2010-08-12 2016-01-26 Schaeffler Technologies AG & Co. KG Method for operating an automated dual-clutch transmission
US8839928B2 (en) 2010-12-02 2014-09-23 Gm Global Technology Operations, Llc Electro-hydraulic control system for a dual clutch transmission
US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
US8904893B2 (en) 2010-12-06 2014-12-09 Gm Global Technology Operations, Llc Method of controlling a dual clutch transmission
US8740748B2 (en) 2010-12-08 2014-06-03 Gm Global Technology Operations, Llc Control system and method for a dual clutch transmission
US8738257B2 (en) 2010-12-08 2014-05-27 Gm Global Technology Operations, Llc Electro-hydraulic control system and method for a dual clutch transmission
US8702564B2 (en) 2010-12-09 2014-04-22 GM Global Technology Operations LLC Electro-hydraulic control system and method for a dual clutch transmission

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CN101029686A (zh) 2007-09-05
EP1826464A3 (de) 2011-01-05

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